US3403722A - Cooling apparatus and process - Google Patents

Cooling apparatus and process Download PDF

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Publication number
US3403722A
US3403722A US557005A US55700566A US3403722A US 3403722 A US3403722 A US 3403722A US 557005 A US557005 A US 557005A US 55700566 A US55700566 A US 55700566A US 3403722 A US3403722 A US 3403722A
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United States
Prior art keywords
cooling
pressure
furnace
inlet
hydrocarbon
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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US557005A
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English (en)
Inventor
Herman N Woebcke
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Stone and Webster Engineering Corp
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Stone and Webster Engineering Corp
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Publication date
Application filed by Stone and Webster Engineering Corp filed Critical Stone and Webster Engineering Corp
Priority to US557005A priority Critical patent/US3403722A/en
Priority to GB9246/68A priority patent/GB1165908A/en
Priority to GB50698/66A priority patent/GB1165905A/en
Priority to FR102974A priority patent/FR1519256A/fr
Priority to IL27809A priority patent/IL27809A/xx
Priority to CH537667A priority patent/CH516129A/fr
Priority to ES339396A priority patent/ES339396A1/es
Priority to AT1042070A priority patent/AT321438B/de
Priority to AT364767A priority patent/AT303774B/de
Priority to BE697761D priority patent/BE697761A/xx
Priority to NL676706069A priority patent/NL151500B/xx
Priority to GR670132928A priority patent/GR32928B/el
Priority to FI125767A priority patent/FI54493B/fi
Priority to NO167963A priority patent/NO120373B/no
Priority to DE1967ST026990 priority patent/DE1551536B2/de
Priority to SE08114/67A priority patent/SE359531B/xx
Priority to SE08115/67A priority patent/SE357354B/xx
Priority to SE08113/67A priority patent/SE357821B/xx
Priority to CS433367A priority patent/CS177854B2/cs
Publication of US3403722A publication Critical patent/US3403722A/en
Application granted granted Critical
Priority to DK566168A priority patent/DK135910B/da
Priority to FR6924783A priority patent/FR2032437A2/fr
Priority to BE736442D priority patent/BE736442A/xx
Priority to DE19691945482 priority patent/DE1945482A1/de
Priority to NO00911/70A priority patent/NO127262B/no
Priority to DK264770A priority patent/DK135472B/da
Priority to US072765A priority patent/US3910347A/en
Priority to FI773454A priority patent/FI773454A/fi
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D51/00—Auxiliary pretreatment of gases or vapours to be cleaned
    • B01D51/10—Conditioning the gas to be cleaned
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10G—CRACKING HYDROCARBON OILS; PRODUCTION OF LIQUID HYDROCARBON MIXTURES, e.g. BY DESTRUCTIVE HYDROGENATION, OLIGOMERISATION, POLYMERISATION; RECOVERY OF HYDROCARBON OILS FROM OIL-SHALE, OIL-SAND, OR GASES; REFINING MIXTURES MAINLY CONSISTING OF HYDROCARBONS; REFORMING OF NAPHTHA; MINERAL WAXES
    • C10G9/00—Thermal non-catalytic cracking, in the absence of hydrogen, of hydrocarbon oils
    • C10G9/14—Thermal non-catalytic cracking, in the absence of hydrogen, of hydrocarbon oils in pipes or coils with or without auxiliary means, e.g. digesters, soaking drums, expansion means
    • C10G9/18—Apparatus
    • C10G9/20—Tube furnaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/005—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for only one medium being tubes having bent portions or being assembled from bent tubes or being tubes having a toroidal configuration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/103—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/12—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically the surrounding tube being closed at one end, e.g. return type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1638—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10G—CRACKING HYDROCARBON OILS; PRODUCTION OF LIQUID HYDROCARBON MIXTURES, e.g. BY DESTRUCTIVE HYDROGENATION, OLIGOMERISATION, POLYMERISATION; RECOVERY OF HYDROCARBON OILS FROM OIL-SHALE, OIL-SAND, OR GASES; REFINING MIXTURES MAINLY CONSISTING OF HYDROCARBONS; REFORMING OF NAPHTHA; MINERAL WAXES
    • C10G2400/00—Products obtained by processes covered by groups C10G9/00 - C10G69/14
    • C10G2400/20—C2-C4 olefins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0075—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for syngas or cracked gas cooling systems

Definitions

  • ABSTRACT OF THE DISCLOSURE A process and apparatus for cooling hot fluid which comprises feeding said fluid through an inlet to an annular cooling chamber, gradually increasing the cross sectional area of the hot fluid while passing from said inlet to said chamber, rapidly cooling and passing the cooled fluid out of the chamber at about the same pressure as the pressure of the fluid at the inlet.
  • the present invention relates to a process for heating a fluid in a conduit and to a process and apparatus for cooling the fluid.
  • the invention relates to a process and apparatus for rapidly cooling a fluid.
  • the invention particularly relates to a process for carrying out hydrocarbon conversion which process comprises heating the hydrocarbon to high temperature, maintaining it at high temperature for a short reaction time and at a low partial pressure and rapidly cooling the hydro carbon to a temperature below which the conversion is carried out.
  • the present invention comprises an apparatus and process which is used to cool rapidly hot fluids.
  • the apparatus comprises a means whereby a hot fluid is contacted on cooling surfaces to provide rapid decrease in the temperature of the hot fluid.
  • the cooling means is suitable for cooling fluidsat elevated pressures.
  • the apparatus of the present invention can be used to cool rapidly hot gases without substantial pressure change.
  • the cooling means has particular and advantageous application when used in conjunction with a process for the production of olefins by cracking hydrocarbon feeds at high temperature and short residence time, using a high temperature radiant heat furnace having relatively short conduits of small diameter.
  • the cooling means is used to provide rapid reduction in the effluent product gas temperature from the furnace without substantial pressure drop.
  • the temperature of the cooling means In cooling high temperature hydrocarbon gas effluents from a hydrocarbon cracking process used to produce olefins, the temperature of the cooling means must be sufliciently low to cool the gases the desired amount and sufliciently high to prevent condensation of high boiling hydrocarbon by-products on the cooling surfaces.
  • Cooling techniques and apparatus of the present invention are particularly useful in cooling the eflluent gases "ice from a process for the thermal cracking of hydrocarbons.
  • the hydrocarbon feed in the process described hereinafter, can be heated to high temperature, maintained at high temperature for a short residence time and selectively converted to desired products.
  • the hot gas reaction products are rapidly quenched or cooled in such a manner that the conversion is substantially stopped after the desired residence time.
  • a particular use for the process described herein is in the high temperature cracking of hydrocarbons to produce olefins, ethylene in particular, and other unsaturated hydrocarbons.
  • a novel furnace In carrying out the thermal cracking of the type de scribed above a novel furnace can be used.
  • the furnace can be used for any desired heating service and in particular for carrying out chemical conversion reactions which require high temperature, short residence time and relatively high mass velocity.
  • a particular use for the novel furnace of the present invention is in carrying out high temperature cracking using hydrocarbon feed.
  • feed or material to be heated is contained within conduits or tubes in the furnace and the tubes are heated by radiant heat.
  • a multiplicity of radiant heat burners are positioned on the walls of the furnace.
  • the furnace of the present invention comprises a convection preheat zone and a radiant conversion zone or cracking zone.
  • the conduits or tubes in which the fluid to be treated is contained are relatively short, of small diameter and of low pressure drop design.
  • the specific operating conditions of the furnace are dependent on the characteristics of the feed stock and the desired products.
  • the length and inside diameter of the conduits or coils in the radiant section are selected to provide the desired residence time and pressure drop.
  • the coils can be disposed vertically or horizontally within the fire box, with two or more tubes connected in series by bends to form a coil. Two or more of such coils can form a coil assembly.
  • the tubes are disposed in the furnace in a plane or planes generally parallel to two facing sides of the fire box, in which sides a plurality of burners is located.
  • Each coil assembly can have its own convection preheat zone and its own quenching or co0lmg zone.
  • the quenching zone is' close coupled to the reaction products outlet from the furnace and provides rapid cooling of the eflluent from the reaction temperature down to a temperature at which the reaction is substantially stopped.
  • the thus cooled eflluent can be cooled further by conventional heat exchange means.
  • Th quenching apparatus and process of cooling of the present invention represent an important part of the overall process. However, the concept used can be readily applied to other processes for cooling hot product streams, for heat recovery and/or for heating fluids.
  • the cooling means and process can be used for rapidly cooling hot gaseous products from other cracking processes.
  • the quenching apparatus provides direct cooling on surfaces.
  • the apparatus is simple in design and easy to operate.
  • the apparatus can be of any size and is normally designed for a specified service.
  • the apparatus can be horizontally or vertically disposed.
  • the cooling unit rapidly cools hot fluids while not substantially changing the pressure of the fluid. That is, the pressure of the cooled fluid at the outlet of the cooling unit is substantially the same as the inlet pressure.
  • the material to be cooled can be upflow or downflow.
  • the operation of the unit can be such that the coolant circulation rate can be self-regulating and within 3 limits adjust itself to the heat load. Alternatively, the coolant circulation rate can be controlled by suitable auxiliary pumping means.
  • the coolant apparatus consists essentially of three concentric pipes, the walls of which form two annular chambers and one central chamber.
  • the cooling fluid can be fed into the top of the unit and flow into the central chamber.
  • the central chamber at the end opposite its inlet is in communication with the first annular chamber.
  • the cooling fluid can flow downward in the central chamber and upward in the first annular chamber and exit through an opening at or near the top of the first annular chamber.
  • the outer wall of the second concentric pipe forms a cooling surface.
  • the hot gaseous material to be cooled can enter at the bottom of the cooling device through an opening in the third concentric pipe and pass upward through the second annular chamber and be cooled by direct contact with the cooling surface.
  • the cooled material can pass out of the cooling device through an outlet located near the top of the second annular chamber.
  • the furnace described can be used for other processes than for cracking of hydrocarbons to olefins.
  • Other quenching means than the described means can be used.
  • the quenching means have specific application to rapid cooling of hot efiluent gas from hydrocarbon cracking furnaces, the cooling means can, of course, be used for other types of cooling service.
  • the cooling means described herein, however, are preferred for rapidly cooling the hot reaction product gases of the present invention.
  • FIGURE 1 is a side elevation of a heating furnace apparatus constructed in accordance with the present invention with part of the side wall broken away to show the inside construction of the furnace.
  • FIGURE 2 is an end elevation of the furnace with part of the end wall broken away to show a section through AA.
  • FIGURE 3 is a side elevation of an embodiment of the cooling or quench apparatus.
  • FIGURE 4 is a section of the cooling apparatus of FIGURE 3 taken through BB showing a cross section of the concentric pipes and cooling tubes.
  • FIGURE 5 is a side elevation of another embodiment of the cooling apparatus.
  • FIGURE 6 is a section of the cooling apparatus of FIGURE 5 taken through CC showing the concentric pipes and cooling fins.
  • FIGURE 7 is a schematic flow diagram showing an embodiment of the overall process and the flow of the various process streams.
  • the process and apparatus of the present invention may use as a feed a material selected to produce specific specialty chemical products.
  • Suitable feed stocks are hydrocarbons which are heated to thermally crack the hydrocarbons.
  • Feeds that can be processed include ethane, propylene, propane, butane, pentane and mixtures of the foregoing, naphtha, gas oil, and crude oil.
  • a particular use of the process and apparatus is to crack petroleum fractions boiling in range of 80 F. to 750 F. to produce olefins.
  • Preferred feeds are petroleum naphtha fractions having initial boiling points in the range of 90 F. to 150 F. and final boiling points in the range of 220 F. to 400 F.
  • the feed is cracked selectively to produce olefins, particularly ethylene, in high yield.
  • the cooling apparatus can use any desired cooling fluid.
  • the cooling fluid can be a liquid that, on heating, partially or completely vaporizes.
  • the preferred cooling fluids are liquids. Suitable liquids are Dowtherm, Aroclors, etc., and water.
  • the preferred cooling liquid is water.
  • the cooling apparatus is used to produce high temperature, high pressure steam.
  • the heat energy recovered in cooling can be used for power generation or heating service.
  • the reactant temperature is made to rise continuously from the inlet of the reaction coil, i.e., in the radiant section of the furnace, to the outlet of the reaction coil.
  • the temperature rise is more rapid at first while the reactants are being heated to the temperature level at which the reaction rates become substantial, and then at a lower rate of increase throughout the remainder of the reaction zone due to the endothermic nature of the cracking reactions.
  • the reactant temperature at the inlet of the reaction zone can be about 1100 to 1200 F. and rises to a value at the outlet of about 1500 to 1650 F.
  • the residence time referred to herein is the residence time of the reactants in the reaction zone.
  • the process of the present invention can be carried out to obtain selective chemical conversions of specific hydrocarbons.
  • the hydrocarbon feed can be in the liquid or vapor phase or mixed liquid vapor phase.
  • the hydrocarbon is normally in vapor phase in the reaction zone.
  • the feed will generally be preheated in the preheat zone from about ambient temperature, e.g., 70 to F. to a temperature below that a which significant reaction takes place, e.g., l100 to 1200 F.
  • the feed may be partially or completely vaporized.
  • steam is added to the feed prior to the feed being introduced to the reaction zone.
  • the steam can be added at points in the preheat section at which the feed is 70 to vaporized.
  • the steam when added in this manner acts to completely vaporize the feed by reducing the hydrocarbon partial pressure.
  • the steam also functions to maintain low hydrocarbon partial pressure in the reaction zone.
  • the process has particular application to thermal cracking of petroleum naphtha fractions in a furnace reactor containing a convection preheat section, and a radiant heat reaction section.
  • the inlet temperature to the radiant heat section will be about 1100 to 1200 F. and the outlet temperature from the radiant heat section will be about 1500 to 1650 F.
  • the feed rate is such that the mass velocity of the feed through the radiant coils in the furnace can be 15 to 35 lbs. per second, per square foot of cross sectional area, preferably, 18 to 26 lbs. per second, per square foot, and specifically 20 to 24 lbs. per second, per square foot of cross sectional area of the reaction tube.
  • the mass velocity when steam is used is based on the total flow of steam and hydrocarbons.
  • thermal hydrocarbon cracking processes at any specified conditions of hydrocarbon charge rate and partial pressure, as the temperature is increased conditions are reached whereby coking of the conduits and/or fouling of the equipment downstream of the furnace occurs thus requiring frequent decoking of the equipment.
  • high temperature process of the present invention higher conversion can be achieved than with conventional, longer time, lower temperature processes, with the result that the yields of ethylene and other unsaturates can be enhanced.
  • the maximum yield of ethylene is increased by increasing the conversion level and by improving selectivity to ethylene.
  • selectivity and yield are enhanced by maintaining a relatively low partial pressure of hydrocarbon in theconversion or reaction zone.
  • the partial pressure in the reaction zone is determined by the total pressure at the furnace outlet, the quantity of dilution steam relative to that of the hydrocarbon and the pressure drop in the cracking coil.
  • the effective average hydrocarbon partial pressure in the reaction zone is lower in a coil which exhibits low pressure drop than in a coil which exhibits high pressure drop.
  • the present invention provides a process and apparatus which utilize relatively short cracking coils, relatively high mass velocity, and relatively low dilution steam ratio, and still achieve low hydrocarbon partial pressure in the reaction zone.
  • the hydrocarbon feed can be diluted with steam at a weight ratio of steam to feed of 0.1 to 2.0, preferably 0.3 to 1.0 and specifically 0.4 to 0.8.
  • the residence time of the feed in the radiant section of the cracking coil can be 0.10 to 0.50 second, preferably, 0.15 to 0.40 second and specifically 0.20 to 0.40 second.
  • the cracking reactions take place very rapidly.
  • the cooling step is carried out very rapidly after the effluent leaves the radiant section of the furnace in about 1 to 30 milliseconds, preferably in about 5 to 20 milliseconds, and specifically in about 5 to 15 milliseconds.
  • the rapid cooling step is critical in the high temperature, short residence time process for cracking hydrocarbons to produce olefins. It is found that, if the cooling step takes substantially more than about 30 milliseconds, there may be substantial coke deposits in interior passages of the cooling unit and downstream equipment.
  • the novel furnace of the present invention can be used to provide heat for any purpose for which it is desired to heat a fluid to high temperature, to maintain the fluid at high temperature for short residence time and at relatively high mass velocity.
  • the furnace comprises a radiant heat section containing radiant burners which provide high temperature over the surface to be heated at high average heat flux of 20,000 to 35,000 B.t.u./hr./sq. ft.,
  • the radiant section of the furnace contains coils or tubes which can have an inlet pressure of 30 to 75 p.s.i.a. and an outlet pressure of 20 to 45 p.s.i.a., and preferably, the inlet pressure can be 40 to 50 p.s.i.a. and the outlet of 25 to 35 p.s.i.a.
  • the pressure drop through the coil is low' and can be to 30 p.s.i. and preferably 10 to tial pressure at the outlet can be about 13 to 14 p.s.i.a.
  • the conduits containing the fluid to be heated can be 60 to 210 ft. in length, each conduit can contain 2 to 8 tubes of 20 to 45 ft. in length connected by 180 bends and the tubes can have an inside diameter of 2-3 inches.
  • the conduifs are about 90 ft. to 150 ft. in
  • the coils are about ft. in length, and comprise three tubes of about 30 ft. in length connected by two bends.
  • the tubes are preferably about 2 inches in inside diameter.
  • the furnace can have a single or a double row of tubes and the tubes can be vertically or horizontally disposed in the furnace.
  • a preferred embodiment of the invention utilizes a single row of veriically disposed tubes.
  • the maximum partial pressure usually occurs at the coil outlet and not in the cracking coil in the zone of high conversion, and in those cases where a maximum does occur in the coil, the maximum partial pressure is not significantly higher than the partial pressure at the coil outlet.
  • the total furnace outlet pressure can be 25 to 30 p.s.i.a.
  • the hydrocarbon partial pressure at the outlet is determined by the amount of dilution steam employed per unit quantity of hydrocarbon and by the molecular weight of the hydrocarbon efliuent.
  • the steam to hydrocarbon weight ratio can be 0.3 to 1.0 and can preferably be about 0.5.
  • the hydrocarbon partial pressure at the coil outlet will be about 14.0 p.s.i.a.
  • reaction rates are so high that the residence time in a quench zone at times as short as 50 millisecond results in a significant amount of reaction taking place. It is, therefore, important to quench the eflluent immediately and very rapidly after it leaves the furnace to a temperature at which substantially no deleterious reaction takes place, e.g., below 1100 to 1400 F.
  • the apparatus comprises a means whereby the hot furnace efiiuent is cooled in an annular passage, either or both of the surfaces comprising the annular passage being a heat transfer surface.
  • This cooling apparatus is particularly adapted to rapid quench of hot gas with a small decrease, substantially no change, or a small increase in the pressure of the fluid being cooled while generating righ pressure steam economically.
  • the cooling apparatus or quenching unit of the present invention provides rapid cooling for hot fluids by direct heat exchange on cooling surfaces.
  • the heat exchanger can be used to cool liquids or gases and/or for heat recovery and generation of steam.
  • the inlet gas temperature to the quench unit can be about 1350 to 1650 F. and is rapidly cooled by 100 to 600 F.
  • the hot gases are fed to the quench unit at a velocity of 350 to 1000 ft./sec., and preferably at 500 to 900 ft./sec.
  • the heat flux at the inlet to the cooling apparatus can be as high as 80,000 B.t.u./hr./sq. ft. and the cooling apparatus can have an average heat flux of about 40,000 B.t.u./hr./ sq. ft.
  • the design and operation of the unit can provide that there be substantially no decrease in pressure between the hot gas inlet and the quenched gas outlet.
  • the pressure decrease of the fluid to be cooled can be kept down to 3 p.s.i. and preferably less than 1 p.s.i.
  • the water is introduced to the unit at a pressure of 1000 to 2000 p.s.i.a.
  • the coolant water is introduced at a pressure of 1500 to 1800 p.s.i.a. and at a temperature of about 595 to 620 F.
  • the circulation rate can be self-regulating within design limits and automatically adjusts for variations in cooling service required.
  • FIGURES 1 and 2 of the drawings show one form of heating apparatus for the heat treatment of fluid materials.
  • the apparatus comprises an enclosure having an outer shell 14 and an inner wall 16 defining a heating chamber 17 and having tubes or pipes 3-6 forming a coil assembly located centrally within said chamber 17. These tubes receive the preheated fluid material to be reacted and form coils Which define paths through which the fluid flows.
  • the furnace wall is made up of the outer shell 14 intermediate block insulation 15 and an inner wall comprised of fire brick 16.
  • the inner wall 16 of chamber 17 comprises a refractory material capable of withstanding the heat to which it may be subjected in any particular installation.
  • Chamber 17 is substantially closed except for passage 13 at its top which forms an outlet for the combustion products leaving the chamber.
  • Passage 13 contains the preheat tubes 7 which communicate with tubes 3-6. Tubes 7 comprise the convection heating section of the furnace and recover heat that may otherwise be wasted.
  • the fluid material to be heated is introduced into line 1, which is in communication with tubes 7, flows through preheat tubes 7, i.e., the convection preheat section, and to the radiant section feed header 2 and flows into the radiant section.
  • the fluid material is thus preheated to a temperature just below that which it is desired to treat or react the material.
  • steam can be introduced into tubes 7 through lines 54 and/or 55, see FIG. 7, to help vaporize the feed and to control the hydrocarbon partial pressure in the radiant section.
  • a multiplicity of radiant burners 18 are located in the opposed side walls of chamber 17 and these burners are arranged in such a manner that radiant heat therefrom is radiated to tubes 3-6.
  • Burners 18 may be supplied in a conventional manner with natural gas or other combustible gas or finely dispersed fuels through headers, manifolds, or individual pipes leading to each burner, which are not shown.
  • the metal case or shell 14 forms the outer wall of the furnace and the complete structure is built on legs 22.
  • Structural members 20 and 21 comprise steel framework which support the furnace walls.
  • radiant heat burner and the details associated therewith need not be described since they are well-known and are conventional in the art. Any type of radiant heat burner can be used which provides substantially all of the heat by radiation.
  • the tubes 3a, b, and c are disposed vertically within the fire box 17.
  • the tubes are about 28 feet in length and are connected in series by two 180 bends to form a single serpentine coil of about feet in total length.
  • the inside diameter of the tubes can be two inches.
  • the coils are supported at the top and guided at the bottom of the furnace in a conventional manner.
  • the inlet tubes of each coil assembly that is, 3a, 4a, 5a and 6a are connected to a feed inlet header 2 at the top of the fire box and the outlet tubes 30, 4c, 50 and 6c are connected to a product outlet header 11 at the bottom of the furnace.
  • the plane of the coil assembly is generally parallel to and equi-distant from two facing sides of the fire box in which sides are located the burners 18, see FIG. 2.
  • coils e.g., 3, 4, 5 and 6 can be connected to one upper header 2 and one lower header 11 and can comprise a coil assembly.
  • a particular furnace can be designed and can contain as many of such coil assemblies as necessary in a single furnace to obtain the desired capacity for the furnace.
  • a coil assembly can contain less than or more than four coils.
  • a furnace can contain from 1 to 20 coil assemblies, and preferably from 4 to 10 coil assemblies.
  • Each coil assembly can be provided with its own convection preheat coil and its own quenching apparatus for the rapid quenching of the efiluent product gases.
  • the combustion gases from convection section pass to a stack which can be common to one or more convection sections.
  • the quenching device or unit must be close coupled to the radiant section coil outlet headers to provide for rapid reduction in temperature of the eflluent gas from the radiant section.
  • Line 12 is in communication with the cooling device and provides a means by which the hot effluent gases from the radiant section of the furnace are conveyed to the cooling device.
  • One embodiment of the present invention comprises the novel quenching device or cooling apparatus.
  • the quenching device is placed in close proximity to the outlet header of the hot effluent stream to be cooled and is designed to rapidly reduce the temperature of the hot eflluent stream by a specified amount.
  • the quenching device represents an important part of the overall process.
  • the inventive concept embodied in the quenching device can find ready application for cooling other process streams and/or to provide for heat recovery.
  • the cooling device can comprise three concentric cylinders or pipes which are vertically disposed, the outer cylinder of which is provided with a multiplicity of equally spaced tubes.
  • the hot efliuent gases are introduced into the coolant apparatus and rapidly cooled by direct heat exchange by contact with two cooling surfaces.
  • the novel cooling apparatus of the present invention provides a means for cooling rapidly the furnace etlluent sufliciently to stop substantially the reactions so that the gas can be conducted to a conventional multitube heat recovery exchanger.
  • the apparatus is a heat exchanger in which high pressure steam is generated.
  • the inlet end of the quencher is designed to lower gradually the velocity of the furnace eflluent stream so that the velocity head or kinetic energy is converted to static pressure.
  • the pressure recovery realized can partially, entirely, or more than offset the friction pressure drop through the device depending upon the specific dimensions of the apparatus and the conditions under which it' is operated. Rapid cooling of the gas is elfected by passing the gas through an annular passage which is cooled.
  • the central concentric pipe 32 has an inlet 73 at its upper end.
  • the second concentric pipe 34 at its upper end just short of inlet 73 curves inward and abuts and terminates at the wall of central pipe 32.
  • the outer wall of pipe 32 and the inner wall of pipe 34 form annular space 33.
  • Spacer 48 maintains pipe 32 equidistant from the inner Wall of pipe 34.
  • Pipe 34 at its lower end forms a rounded chamber terminating in rounded end member 37.
  • the third concentric pipe 36 extends about the length of the apparatus and terminates short of the top of pipe 34. Above the point a which pipe 36 terminates, conduit 74 is in communication with annular space 33 through outlet opening 75.
  • the inner wall of pipe 36 and the outer Wall of pipe 34 form the second annular chamber 35.
  • baffle ring 46 which prevents stagnant product gases from accumulating in the upper end of the annular chamber. Also near the top of annular chamber 35 there is provided connecting means 44 which is in communication with annular passage 35 through outlet opening .45. Baffle ring 46 and spacers 47 maintain concentric pipe 34 in the center of annular chamber 35.
  • the outer wall of concentric pipe 36 can be provided with a multiplicity of equally spaced tubes 61 which'tubes are connected to and are in close contact with outer wall 36. These tubes run the approximate length of outer wall 36 from about the bottommost portion of Wall 36 up to conduit 44. Tubes 61 at the upper and lower ends flare outward by curved portions 60 and 62, respectively and are in communication with torus 50 at their upper end and torus 49 at their lower end. Torus 49 has a connecting conduit 64 through which coolant fluid passes through inlet 63 into the torus 49 and flows upwardly through tubes 61. Tubes 61 are in communication with upper torus 50 and the cooling fluid flows out of torus 50 through outlet 66 and conduit 65.
  • nose cone 38 which is attached to end member 37 and converges downwardly to form the nose cone.
  • Concentric pipe 36 at a position proximate to the end of the straight portion of concentric pipe 34 tapers inwardly in the general direction of the nose cone 38 to form inlet opening 43.
  • the cross sectional area of inlet 43 is such that the annular passage 40 gradually increases in cross sectional area from inlet 43 to the annular space formed by the walls of pipes 34 and 36.
  • the cooling apparatus can be designed and sized to accommodate any desired cooling service. Suitable apparatus for use in the present invention can have an overall length of the cooling apparatus from coolant inlet 73 to hot efiluent gas inlet 43 of 20 to 24 feet.
  • the inside diameter of the third concentric pipe can be 8 to 10 inches.
  • Tubes 61 can be about one to two inches in inside diameter.
  • the inside diameter of toruses 49 and 50 can be about 3 to 4 inches.
  • the cross sectional area of central chamber formed by pipe 32. can be seven square inches.
  • the length of the central chamber can be 18 to 20 feet.
  • the cross sectional area of the first annular chamber 33 can be about twelve square inches and can have a length of about 18 to 20 feet.
  • the cross sectional area of the second annular chamber 35 can be about 20 square inches and the chamber can have :a length of about 16-18 feet, excluding the inlet section.
  • the cross sectional area of gas inlet 43 can be about 12 to 13 square inches, gradually increasing in cross sectional area to about 19 to 20 square inches in the straight portion of pipe 34.
  • Tapered nose cone 38 can have an angle at its apex of about 28 to 30.
  • the total cross sectional area of tubes 61 can be about 10-11 square inches.
  • the total coolant flow through tubes 61 and first annular passage 33 can be about 10 times the flow of hot efliuent gases based on weight.”
  • the coolant water is introduced through inlet 73 and flows downward in the central chamber of concentric pipe 32 and .a mixture of water and steam flows upward in first annular passage 33 and passes out near the top of the first annular passage through outlet opening 75.
  • Coolant water enters the bottom torus 49 through inlet 63 and flows upward in tubes 61 providing direct contact cooling for the hot furnace efiiuent gases at the inner wall surface of pipe 36.
  • the inner surface of pipe 36 and the outer surface of pipe 34 provide the two cooling surfaces for the hot gas.
  • the inlet diffuser or nose cone 38 provides for gradual increase in cross sectional area of the gases entering through inlet 43 which gradually increases the pressure of the hot gases as the gas velocity is reduced.
  • the diffuser cone 38 insures uniform gas distribution between cooling surfaces 36 and 34 without the production of eddy currents in the gas flow.
  • the pressure increase in the gas caused by the gradual increase in cross sectional area in the inlet compensates for a substantial portion of the pressure loss in the gas due to friction.
  • the cooled outlet gas pressure will be about the same as the hot inlet gas pressure.
  • Passage 40 is sized to provide the gradual increase in cross sectional area through which the hot gases flow. The gradual increase is provided by the tapered shape of nose cone 38 and the converging wall 39 of pipe 36.
  • the gradual increase in cross sectional area provides a gradual decrease in gas velocity which is accompanied by an increase in gas pressure to conserve total energy.
  • the angle of nose cone 28 and the entering pipe 39 are selected so that the increase in cross sectional area of the annular space formed between cone 38 and pipe 39 per unit length is equal to the increase in cross sectional area per unit length of a conical pipe having an angle of divergence of 4 to 7, e.g., 5.
  • the angle of the cone 3'8 and the extent to which converging wall 39 corresponds to the angle of cone 38 provide the necessary gradual increase in cross sectional area.
  • the nose cone angle can be 25 degrees to 30 degrees.
  • the angle of converging wall 39 if taken to an apex can be 20 to 25 degrees.
  • the length of cone 38 can be 8 to 12 inches.
  • the cooling chamber that is the second annular chamber 35 has the same cross sectional area throughout its length.
  • FIGURE 4 shows a cross section of the cooling apparatus taken through line B-B of FIGURE 3.
  • FIGURE 4 shows an end section of tubes 61 and the manner in which they are connected by welds 70 to the outer wall of concentric pipe 36.
  • a suitable heat transfer material 71 can be used to fill the space between tubes 61 and to improve the heat transfer between the hot gases and coolant.
  • FIGURES 5 and 6 of the drawings Another embodiment of the cooling apparatus is illustrated by FIGURES 5 and 6 of the drawings.
  • cooling of the hot gases is provided primarily by direct contact with the outer wall of concentric pipe 34.
  • pipe 34 can contain a multiplicity of cooling fins 56 which project into the hot gases in annular space 35.
  • a petroleum naphtha fraction boiling in the range of to 375 F. is fed through line 1 into convection preheat section 7 wherein it is heated from about ambient temperature to a temperature of about 1000 to 1100 F.
  • Steam, at a ratio of steam to hydrocarbon of about 0.4 to 0.8 by weight, is introduced into preheat section 7 at a point where the naphtha feed is approximately 90% vaporized.
  • the preheated hydrocarbon and steam mixture at about 1000 to 1100 F. it then fed into the inlets of coils 3-6.
  • the feed is heated in the coils from about 1000 to 1100 F. to a coil outlet temperature of about 1650 F.
  • the hydrocarbon partial pressure at the coil outlet is about 12 to 14 p.s.i.a.
  • the residence time of the fluid in the radiant section of the furnace is about 0.20 to 0.25 second.
  • the mass velocity of the hydrocarbon and steam in the coils is about 18 to 26 pounds per second, per square foot of cross sectional area of the coil.
  • the radiant coil inlet pressure is about 45 p.s.i.a. and the coil outlet pressure of the efiiuent gases is about 25 p.s.i.a.
  • the hot efiluent gases are fed through line 12 to the cooling apparatus at a gas velocity of about 800 ft./ sec.
  • the hot gases are introduced into the cooler through inlet 43 at a temperature of about 1650 F.
  • the cooled gases are withdrawn from the cooler through outlet 45 which is in communication with line 107.
  • the gases are cooled rapidly in about 10-20 milliseconds to a temperature of about 1200 to 1400 F. and are conveyed to a conventional cooling means for further cooling and to a conventional olefin separation plant for separation and recovery of ethylene.
  • the gas pressure in line 107 is about 25 p.s.i.a.
  • FIGURE 7 of the drawing illustrates the thermosiphon cooling embodiment of the present invention.
  • Coolant water from steam drum 100 is introduced through line 103 and line 108 at a temperature of about 600 F. and a pressure of about 1600 p.s.i.a.
  • the coolant flows through line 108 into torus 49 and upward in tubes 61 in which tubes it is partially converted to steam.
  • the steam and water mixture fiows into torus 50 and through lines 106 and 104 back to steam drum 100.
  • a steam and water mixture from first annular passage 33 (see FIGURE 3) flows out of outlet 75 into line 105 and 104 and back to steam drum 100.
  • the water being more dense than the mixture of steam and water sets up a thermosiphon flow of coolant water through the cooling apparatus.
  • the cooling apparatus is self-regulating and the higher the temperature and flow rate of gases into the cooling unit the faster will be the coolant liquid circulation rate.
  • Saturated steam at a temperature of about 600 F. and a pressure of about 1600 p.s.i.a. can be withdrawn from steam drum 100 through line 101 and the heat energy recovered.
  • Boiler feed water is fed to steam drum 100 through line 102.
  • the process and apparatus of the present invention can be used in other known processes.
  • the furnace and process of using the furnace has many obvious applications for heating fluids and/or carrying out specific chemical reactions.
  • the cooling apparatus similarly has many obvious uses for cooling process streams, heat exchange, and other uses that will appear obvious to those skilled in the art.
  • the coil outlet temperature of the efiiuent gases is about 1625 F. at an outlet pressure of about 25 p.s.i.a. and hydrocarbon partial pressure of about 12 p.s.i.a.
  • the efiiuent gases are rapidly cooled from about 1625 F. to about 1200 F. in less than about 15 milliseconds.
  • the quencher outlet pressure of the cooled gas is about 24 p.s.i.a. Coolant, water having an inlet temperature of about 600 F. and a pressure of about 1600 p.s.i.a. is circulated at a'ratio of coolant to hot gas of about 10 to 1 by weight.
  • the temperature of the steam-water mixture leaving the quencher is about 600 F. and about 1 pound of steam is formed for. each 15 pounds of water circulated.
  • the product distribution of the effluent gases is as follows:
  • EXAMPLE 2 In another example of the invention a naptha fraction derived from a Nigerian crude oil is thermally cracked to produce olefins.
  • the fraction has the following characteristics.
  • Steam is mixed with the hydrocarbon feed at a weight ratio of steam to hydrocarbon of 0.5.
  • the mixture is heated in the preheat section to about 1100" F. and introduced into the cracking coils at an inlet pressure of about 43 p.s.i.a.
  • About 1150 pounds of hydrocarbon feed per hour, per coil or about 4600 pounds per hour per assembly of four coils are fed to the furnace.
  • the steam and hydrocarbon mixture is gradually heated from about 1100 F. to a coil outlet temperature of about 1645 F.
  • the feed is thermally cracked in the coil at a residence time of 0.25 second.
  • the feed undergoes thermal cracking under conditions of high severity and low hydrocarbon partial pressure to produce ethylene in high yield. Based on a single pass about 24% yield by weight is obtained.
  • the coil outlet temperature of the effluent gases is about 1645 F. at an outlet pressure of about 25 p.s.i.a. and a hydrocarbon partial pressure of about 14 p.s.i.a.'
  • the effluent gases are rapidly cooled from a temperature of about 1645 F. to about 1200 F. in less than about 15 milliseconds.
  • the quencher outlet pressure of the cooled gas is about 24 p.s.i.a.
  • the operating conditions of the quencher unit are about the same as in Example 1.
  • This example illustrates the conversion and product distribution obtained from a naphtha feed which contains a relatively large amount of naphthenes as compared to the naptha feed of Example 1 which contains a relatively large amount of parafiins.
  • the cracking furnace used to illustrate the above examples contains radiant section coils having an inside diameter of about two inches.
  • Each coil comprises three tubes of about equal length joined by two 180 bends to form a coil of about 90 feet in length.
  • a process for cooling hot fluid which comprises feeding said hot fluid through an inlet means in communication with a single annular chamber, the hot fluid in passing from the inlet to the entrance of the annular chamber gradually increasing in cross sectional area, at least one surface of said chamber being cool, rapidly cooling said fluid by indirect heat exchange with a coolant and passing said fluid out of said annular chamber at about the same pressure as at said inlet.
  • a process for cooling hot gases which comprises feeding said hot gases through an inlet means in communication with a single annular chamber, at least one surface of said chamber being cool, the flow of said gases from the inlet to said annular chamber being substantially turbulence-free, rapidly cooling said gases in said annular chamber, and passing said cooled gases out of said annular chamber.
  • a process for cooling hot fluid which comprises feeding said hot fluid through an inlet means in communication with a single annular chamber, at least one surface of said chamber being cool, the hot fluid passing from the inlet to the entrance of the annular chamber gradually increasing in cross sectional area, gradually decreasing in linear velocity, and gradually increasing in pressure, rapidly cooling said fluid in said annular chamher, and passing said cooled fluid out of said annular chamber at about the same pressure as at said inlet.
  • a process for cooling hot gases which comprises feeding said hot gases through an inlet means in communication with a single annular chamber, the hot gases passing from said inlet to said annular chamber gradually increasing in cross sectional area, said increase per unit length being equal to the increase in cross section area per unit length of a conical pipe having an angle of divergence of 4 to 7, at least one surface of said chamber being cool, rapidly cooling said fluid by indirect heat exchange with a coolant and passing said fluid out of said annular chamber at about the same pressure as at said inlet.
  • a process for cooling hot effluent gases from a hydrocarbon cracking process to produce olefins which comprises feeding said gases at a temperature of 1350 to 1650 F. through an inlet means in communication with a single annular chamber, at least one surface of said chamber being cool, the hot gases passing from said inlet to said annular chamber being substantially free of turbulence, said gases gradually increasing in cross sectional area, and gradually decreasing in linear velocity, rapidly cooling said gases by about to 600 F. in about 5 to 15 milliseconds, and passing said cooled gases out of said annular chamber at about the same pressure as at said inlet.
  • coolant comprises water which is indirectly contacted with said hot fluid at a pressure of 1000 to 2000 p.s.i.a. and at a temperature of about 540 to 635 F.
  • a process for cooling hot effluent gases from a hydrocarbon cracking process which comprises indirect heat exchange between said hot gases and a cool-ant comprising introducing said hot gases through an inlet means in communication with a single annular chamber at a linear velocity of about 700 to 800 ft./sec. and at a temperature of about 1350 to 1650 F., and rapidly cooling said gases by about 100 to 600 F. to about 1200 to 1400 F. in about 1 to 30 milliseconds.
  • hydrocarbon effluent is from a process for producing olefins and said hot gases are introduced to said annular chamber at a temperature of about 1500 to 1650 and are rapidly cooled by about 100 to 600 F. in about 5 to 15 milliseconds.
  • hot gas effluent is from a hydrocarbon cracking process to produce ethylene.

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  • Engineering & Computer Science (AREA)
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  • Oil, Petroleum & Natural Gas (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Geometry (AREA)
  • Organic Chemistry (AREA)
  • Production Of Liquid Hydrocarbon Mixture For Refining Petroleum (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
US557005A 1966-06-13 1966-06-13 Cooling apparatus and process Expired - Lifetime US3403722A (en)

Priority Applications (27)

Application Number Priority Date Filing Date Title
US557005A US3403722A (en) 1966-06-13 1966-06-13 Cooling apparatus and process
GB50698/66A GB1165905A (en) 1966-06-13 1966-11-11 Process for Cooling Fluids
GB9246/68A GB1165908A (en) 1966-06-13 1966-11-11 Heat Exchange Apparatus
IL27809A IL27809A (en) 1966-06-13 1967-04-17 Cooling apparatus and process
FR102974A FR1519256A (fr) 1966-06-13 1967-04-17 Appareil et procédé de refroidissement
CH537667A CH516129A (fr) 1966-06-13 1967-04-17 Procédé de refroidissement d'un fluide et appareil de refroidissement pour sa mise en oeuvre
ES339396A ES339396A1 (es) 1966-06-13 1967-04-17 Procedimiento y aparato para enfriar gas efluente de un proceso de pirolisis de hidrocarburos.
AT1042070A AT321438B (de) 1966-06-13 1967-04-18 Verfahren zum Wärmeaustausch bei strömenden Medien
AT364767A AT303774B (de) 1966-06-13 1967-04-18 Wärmeaustauschvorrichtung
BE697761D BE697761A (de) 1966-06-13 1967-04-28
NL676706069A NL151500B (nl) 1966-06-13 1967-04-28 Inrichting voor het afkoelen van een heet stromend gas.
GR670132928A GR32928B (el) 1966-06-13 1967-04-29 Συσκευη και μεθοδος ψυξεως.
FI125767A FI54493B (fi) 1966-06-13 1967-04-29 Foerfarande och anordning foer kolvaetets termiska omvandling till olefiner
NO167963A NO120373B (de) 1966-06-13 1967-05-02
DE1967ST026990 DE1551536B2 (de) 1966-06-13 1967-06-09 Waermeaustauscher zum kuehlen von heissen gasen
SE08114/67A SE359531B (de) 1966-06-13 1967-06-09
SE08115/67A SE357354B (de) 1966-06-13 1967-06-09
SE08113/67A SE357821B (de) 1966-06-13 1967-06-09
CS433367A CS177854B2 (de) 1966-06-13 1967-06-13
DK566168A DK135910B (da) 1966-06-13 1968-11-20 Varmeudvekslingsapparat til hurtig afkøling af varme fluida.
FR6924783A FR2032437A2 (en) 1966-06-13 1969-07-21 Heat exchanger for furnace gases
BE736442D BE736442A (de) 1966-06-13 1969-07-23
DE19691945482 DE1945482A1 (de) 1966-06-13 1969-09-09 Waermetauscher und Verfahren zum Kuehlen von heissen Gasen
NO00911/70A NO127262B (de) 1966-06-13 1970-03-13
DK264770A DK135472B (da) 1966-06-13 1970-05-22 Fremgangsmåde til afkøling af varme fluida, især varm udstrømningsgas fra en carbonhydridkrankningsproces.
US072765A US3910347A (en) 1966-06-13 1970-09-16 Cooling apparatus and process
FI773454A FI773454A (de) 1966-06-13 1977-11-16

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US557005A US3403722A (en) 1966-06-13 1966-06-13 Cooling apparatus and process

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US3403722A true US3403722A (en) 1968-10-01

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US (1) US3403722A (de)
AT (2) AT303774B (de)
BE (1) BE697761A (de)
CH (1) CH516129A (de)
DE (1) DE1551536B2 (de)
ES (1) ES339396A1 (de)
GB (2) GB1165908A (de)
GR (1) GR32928B (de)
IL (1) IL27809A (de)
NL (1) NL151500B (de)
NO (2) NO120373B (de)
SE (1) SE357821B (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2032438A1 (de) * 1969-02-27 1970-11-27 Stone & Webster Eng Corp
US5427655A (en) * 1990-11-29 1995-06-27 Stone & Webster Engineering Corp. High capacity rapid quench boiler
US5981818A (en) * 1995-03-21 1999-11-09 Stone & Webster Engineering Corp. Integrated cracking and olefins derivative process utilizing dilute olefins
US20110065973A1 (en) * 2009-09-11 2011-03-17 Stone & Webster Process Technology, Inc Double transition joint for the joining of ceramics to metals
US20110197830A1 (en) * 2008-09-09 2011-08-18 Brueckner Jan Continuous steam generator
WO2024025988A1 (en) 2022-07-28 2024-02-01 Chevron Phillips Chemical Company, Lp Flexible benzene production via selective-higher-olefin oligomerization of ethylene

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3238513A1 (de) * 1982-10-18 1984-04-19 Anton Steinecker Maschinenfabrik Gmbh, 8050 Freising Doppelrohr-waermetauscher
ES2428942B1 (es) * 2013-08-07 2014-09-29 Abengoa Hidrógeno, S.A. Generador de vapor de agua

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2475025A (en) * 1946-10-26 1949-07-05 Universal Oil Prod Co Reactor for close temperature control
US3144080A (en) * 1961-03-02 1964-08-11 Schmidt Sche Heissdampf Heat exchanger for the cooling of freshly cracked gases or the like

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2475025A (en) * 1946-10-26 1949-07-05 Universal Oil Prod Co Reactor for close temperature control
US3144080A (en) * 1961-03-02 1964-08-11 Schmidt Sche Heissdampf Heat exchanger for the cooling of freshly cracked gases or the like

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2032438A1 (de) * 1969-02-27 1970-11-27 Stone & Webster Eng Corp
US3583476A (en) * 1969-02-27 1971-06-08 Stone & Webster Eng Corp Gas cooling apparatus and process
US5427655A (en) * 1990-11-29 1995-06-27 Stone & Webster Engineering Corp. High capacity rapid quench boiler
US5981818A (en) * 1995-03-21 1999-11-09 Stone & Webster Engineering Corp. Integrated cracking and olefins derivative process utilizing dilute olefins
US20110197830A1 (en) * 2008-09-09 2011-08-18 Brueckner Jan Continuous steam generator
US9267678B2 (en) * 2008-09-09 2016-02-23 Siemens Aktiengesellschaft Continuous steam generator
US20110065973A1 (en) * 2009-09-11 2011-03-17 Stone & Webster Process Technology, Inc Double transition joint for the joining of ceramics to metals
US9011620B2 (en) 2009-09-11 2015-04-21 Technip Process Technology, Inc. Double transition joint for the joining of ceramics to metals
WO2024025988A1 (en) 2022-07-28 2024-02-01 Chevron Phillips Chemical Company, Lp Flexible benzene production via selective-higher-olefin oligomerization of ethylene

Also Published As

Publication number Publication date
AT321438B (de) 1975-03-25
CH516129A (fr) 1971-11-30
NO120373B (de) 1970-10-12
DE1551536A1 (de) 1970-04-02
BE697761A (de) 1967-10-30
ES339396A1 (es) 1968-05-01
DE1551536B2 (de) 1977-07-07
GR32928B (el) 1967-10-05
GB1165908A (en) 1969-10-01
AT303774B (de) 1972-12-11
NL151500B (nl) 1976-11-15
NO127262B (de) 1973-05-28
IL27809A (en) 1971-10-20
GB1165905A (en) 1969-10-01
SE357821B (de) 1973-07-09
NL6706069A (de) 1967-12-14

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